Transmission



Dec- 27 E966 R. H. SCHAEFER ETAL 3,293,934

TRANSMI SSION Filed Sept. '25, 1962 INVENTORS ATTORNEY United StatesPatent 3,293,934 TRANSMSSION Robert H. Schaefer, Westfield, and Mark E.Fisher,

Carmel, 1nd., assignors to General Motors Corporation, Detroit, Mich., acorporation of Deiaware Filed Sept. 25, 1962, Ser. No. 226,021 12Claims. (Cl. 74-472) This invention relates to transmissions andparticularly to a control system for power shifting transmission.

The control system is employed with a transmission having la torqueconverter and lookup clutch, a two-speed splitter gear unit and a threespeed and reverse main gear unit. The two speed splitter gear unitprovides a low and a high drive ratio in each of the ratios of the maingear y unit to provide six forward d-rive ratios and two reverse driveratios. The torque converter provides additional torque multiplicationduring each ratio change and until a proper output speed is reached ineach ratio, then the lookup clutch is engaged to provide a lookup driveto the gearing. A manual selector valve having a single valve element,movable to a plurality of ratio positions, supplies uid from the mainline in each position to a selected pair of iiuid operated ratioengaging devices each consisting of a fluid motor tand a frictiondevice, one being in the splitter gear unit and the other being in themain gear unit, to provide each ratio. The valve element has alongitudinally extending supply passage and exhaust passage eachprovided with a plurality of slot ports cooperating with annular portsin the valve bore in the valve body t=o provide the connections in theproperly selected pairs for operating the fluid operated ratio eng-agingdevices. In order to provide torque converte-r operation in each ratio,the lookup control valve operation by the splitter gear unit outputgovernor pressure is modified -by the splitter high engaging pressure sothat the lookup clutch is engaged at a low speed when the transmissionis in splitter lo-w and at a relatively higher speed when thetransmission is in splitter high.

An object of the invention is to provide in a transmission having adrive train including a torque converter, a lookup clutch, a splittergear unit and a main gear unit, a control system having ra manualselector valve with a movable valve element having a longitudinal fluidsupply bore and 'a longitudinal exhaust bore and movable to a pluralityof positions to supply fluid to engage selected pairs of' the ratioengaging devices in each of the splitter gear unit and the main gearunit to `provide a drive ratio in each position and a lookup shift valveoperative to engage the lookup clutch when the splitter gear unit is inlow ratio at a low speed and to eng-age the lookup clutch whenever thesplitter gear unit is in high speed at a higher speed to provideconverter drive at a particular converter speed in each drive ratio.

Another object of the invention is to provide in a transmission having aplurality of fluid operated ratio engaging devices engageable in pairs-to provide a plurality of drive ratios, a selector valve having asingle valve element axially movable in a bore to :a plunality ofpositions and the valve element having an axial fluid supply passage andan axial exhaust passage with a plurality of slot ports in the valveelement cooperating with a plurality of annular ports in the valve bodyto connect the fluid supplied to a plurality of pairs of said fluidoperated ratio engaging devices.

Another object of the invention is to provide in a transmission havingia drive including a torque converter and lookup clutch and gear unit, agear unit output governor controlling a lookup shift valve to engage alookup clutch during the operation of the transmission in each ratio andmeans controlled by the ratio select-or mechanism opera- Patented Dec.27, 1966 tive on the lookup shift valve to provide for the engagement ofthe lookup clutch at a low gear unit output speed in low ratio and at ahigher gear unit output speed in a higher ratio.

These and other objects of the invention will he more apparent from thefollowing description and drawing of a preferred embodiment of theinvention, illustrated in the accompanying drawing.

FIGURE 1 is schematically illustrates the transmission gearing andcontrols.

FIGURE 2 is a partial sectional view on the line 2 2 of FGURE l showinga section of the manual selector valve.

The invention is illustrated in a transmission having an input shaft 3driving a rotary torque converter Ihousing 4. The torque converterhousing 4 encloses the torque converter rotors, the pump 5, the stator6, which may be -a dual stator each connected by a one-way brake to thestationary transmission housing 8, and the turbine 9 connected by a hub10 to the converter shaft 14. The duid in the torque converter iscirculated by the pump 5 through the turbine 9 and redirected by thestator 6 for entry to the pump to provide fluid torque multiplicationdrive in a conventional manner. The lookup clutch 11 has driving .platesmounted on the rotary housing 4 and a driven plate connected to the hub10, and operates on the supply of fluid to the lookup clutch motor 12 toengage the clutch 11 :and connect the input shaft 3 to the :convertershaft 14 to -lockup the torque converter and substitute a directmechanical drive for the liuid torque multiplying drive of the torqueconverter.

The converter shaft 14 drives a hub assembly 16 on which thehydrodynamic brake rotor 17 is mounted between the stators 18 which arefixed to the stationary housing 8.

The converter shaft 14 is :connected by two speed splitter gear unitproviding underdrive or low and direct or high to the 4intermediateshaft 24. The splitter gear unit has a ring .gear 19 driven by theconverter shaft 14 through hub 16 which meshes with planetary pinion 21mounted on the carrier 22 which is connected to drive the intermediateshaft 24. The sun =gear 20- is controlled to provide the two drivesthrough the control hub 26 which for low is held stationary by the brake27 consisting of a plurality of pilates attached alternately to the hub26 and the housing 8 and engaged by the splitter low lmotor 28. Toprovide high, the control hub I26 is connected by the clutch 29 havingalternate plates attached to the control hulb and the carrier 21 andactu-ated by the splitter yhigh fluid motor 31.

The main gear unit provides low, intermediate, high and reverse drives.The low ratio tdrive is provided between the intermedi-ate shaft 24 andthe output shaft 37 by the low planetary lgear set consisting of aplurality of planetary pinions 35 mounted on a carrier 36 connected tothe output shaft 37 and meshing with the driving sun gear 33, fixed t-othe intermediate shaft 24, and with the controlled ring gear 38. Thering gear 38 is 'controlled by a ybrake 39 consisting of alternateyplates attache-d to the ring ygear and the -housing 8 which are engagedby the low motor 41 to hold the rin-g gear for low ratio.

Intermediate ratio in the main gear unit is provided by the intermediateand low gear sets. The intermediate gear set has pinions 44 mounted on acarrier 4S connected to ring gear 38 and meshing with a larger sun gear43 driven by the intermediate shaft 24 and the controlled ring gear 46.To provide intermediate ratio the ring gear 46 is held by the brake 47consisting of alternate plates attached to the ring gear 46 and thehousing and engaged by the intermediate motor 48 to drive ring gear 38of tihe low gear set so the combined gear sets provide intermediater-atio.

yHigh ratio in the main gear unit is a direct drive provided by lockingup the main gear unit. The intermediate shaft 24 is connected to theclutch hub `51 and connectable by the clutc-h 52 to the carrier 45. Thehigh clutch motor 53 is actuated to engage the plates of clutch 52attached to both the hub 51 and the carrier 45 to cause the carrier 45to rotate with the intermediate shaft 24 -and 'lock -up :the main gearunit for direct drive.

Reversedrive is provided yby the reverse :gear set which has a pluralityof pinions 57 rotatably mounted on a carrier 58 connected to drive theoutput shaft 37 and meshing with a sun gear 56 connected to rotate withthe ring gear 38 and meshing with a ring giear 59. The brake 61 f-orcontrolling ring gear 59 consists of plates connected to the ring gearand Ihousing 8 and is actuated by a reverse fluid motor 62 to hold thering gear to provide reverse drive in the main gear unit.

In the splitter gear unit, either the splitter low motor or the splitterhigh motor are supplied with fluid to selectively provide either low orhigh ratio in the splitter gear unit, and the other motor is connectedto exhaust. In the main gear unit fluid is selectively supplied to oneof the low, intermediate, high and reverse motors and the others areexhausted to provide the selected one of the low, intermediate, high andreverse ratios. The controls permit engagement of reverse ratio of themain unit with either low or high in the splitter unit t-o provide areverse low RL and a reverse high RH. Also, when the main unit is in lowratio, either low or high splitter gear unit may be engaged to providerespectively lst and 2nd forward drive ratio. Similarly, withintermediate engaged in the main unit, `low and high in the splitterunit provide 3rd and 4th ratio. With high in the main unit, splitter lowand splitter high provide th and 6th ratio. Each of the fluid actuatedratio engaging friction devices consisting of a motor for actuating aratio engaging clutch or brake is provided with suitable retractionsprings (not shown) to disengage the clutch or brake on exhausting thecontrol line connected to each motor. The lockup clutch motor may havesuitable retraction springs or be disengaged by the fluid pressure inthe torque converter housing.

Control system The fluid which exhausts from the various exhaust portsEX, the lubrication system and other leakage collects in the sump 76located in the lower portion of the stationary transmission housing 8.The front pump FP supplies fluid via the front pump line 77 and the rearpump RP supplies fluid via the Vrear pump line 78 and check valve 79 tothe main line 81.

The pressure in main line 81 is regulated by the main line regulatorvalve 82 which has a valve element 83 Ihaving lands a, b, c of equaldiameter and land d of smaller diameter located in a stepped bore 84 inthe valve body. In the closed position shown, main line 81 is connectedby port 86 to the space between land b and c and passes through theaperture 87 in land c to act on the unbalanced area between land c and dto bias the valve element 83 upwardly against the dual spring 89. As thepressure in main line 81 reaches the regulated value the valve elementmoves upwardly against the biasing force of the springs 89 and connectsport 86 to the converter and brake feed line 91 which, as explainedbelow, provides the feed for both the converter and brake after the mainline has reached regulated pressure. The orifice 87 in land c or otherflow restricting means bypassing land c damps the regulating action ofthe valve. When the main line and converter brake feed line 91 are atregulated pressure, further excess fluid supply in main line 81 willraise the valve further so that main Iline port 92 is directly connectedto exhaust port 93.

The regulated main line pressure may be increased or decreased by thefollowing control functions. The throttle pressure which is controlledby throttle valve 116 proportional to torque demand or the throttlepedal position, described below, is supplied by line 96, through orifice97 which damps the regulating action of throttle pressure, to a bore 98where the throttle pressure acts on the piston 99 which engages thevalve element 83 to increase the main line regulated pressure withincreasing torque demand. The brake outlet line 101 is connected bybranch 102 to the spring chamber to act downwardly on the land a of thevalve element 83 tending to increase the main pressure, and the brakeoutlet line branch 103 is connected to act upwardly on the land d todecrease the pressure a lesser amount to provide a net increase in mainline pressure with increasing brake outlet pressure. As is known in theart, the brake outlet line 101 is connected to the brake operatingchamber radially outward from the rotor 17 by means of a centrifugaltype outlet as employed in centrifugal pump so that the pressure in line101 will be proportional to the braking torque being absorbed by thehydrodynamic brake. The lockup shift line 106 is connected to bore 107to act on the land a of plug 108 to urge valve element 83 upwardly toreduce main line pressure whenever the lockup shift valve has shifted tosupply fluid to the lockup shift line 106. In intermediate ratio, theintermediate line 184 is connected to bore 107 above land a to actdownwardly on land a with a reduced force to reduce the degree ofpressure reduction due to lockup shift line pressure when inintermediate ratio.

The main line 81 is also connected to the throttle valve 116 which has avalve element 117 having lands a and b located in a bore 118. Theactuating rod 121, whose position is controlled by the position of theaccelerator pedal or in accordance with fuel supply demand varies thepressure of spring 122 acting on the throttle regulator valve 117 toprovide a pressure in throttle pressure line 96 proportional to throttlepedal position or torque demand. This valve operates in a conventionalmanner with the spring 122 biasing valve element 117 to the openposition where the main line 81 is connected between the lands a and bto port 123 to supply throttle pressure line 96. Line 96 is connected byport 124 to act on the unbalanced end area of land a to oppose thebiasing force of the spring to move the valve toward the exhaustposition blocking line 81 and connecting throttle valve line 96 via port123 to exhaust 126. Exhaust 127 vents the spring chamber portion of thebore 118.

The main line 81 is also connected through the orifice 131 at the lockupclutch cutoffvalve 132 to the ratio supply line 133 which supplies fluidto all ratio engaging motors. The lockup clutch cutoff valve 132 has avalve element having lands a and b of equal diameter located in a bore136. The valve element 134 is biased to the position shown Iby thespring 137 connecting the lockup shift line 106 supplied by the lockupshift valve to the lockup clutch line 111 which is connected to thelockup clutch motor 12 to engage the lockup clutch. When there is flowfrom the main line 81 through the orice 131 to the rati-o supply line133 to supply ratio motor for engagement, the higher pressure in thechamber 141 on the upstream side of orifice 131 overcomes the spring andthe lower pressure in the chamber 142 at the other end of the valvesupplied by port 143 on the downstream side of orifice 131 to move thevalve element 134 downwardly blocking lockup shift line 106 andconnecting lockup clutclr line 111 to exhaust 144 to disengage thelockup clutc The manual selector valve 151 has a valve element 152 ofuniform diameter axially slidable in a bore 153. The valve element 152has a pair of cored or drilled passages, the supply passage 156 isblocked at both ends and has a series of supply ports a, b, c, d, e, jand g and the ex-y exhaust ports h, i, j, k and l. The ports aretransverse slots intersecting one of the passages. The valve bore 153has a series of annular feed ports comprising successively a doublewidth port 161, single width ports 162, 163, 164, 165, 166, 167, 168,169, 171 and double width ports 172, 173, 174` and 175. The ratio supplyline 133 is connected to the double width feed port 161. The splitterlow line 181 connected to splitter low motor 28 is connected to thesingle width feed ports 162, 164, 166, 168 and 171. The splitter highline 182 connected to the splitter high motor 31 is connected to thesingle width feed ports 163, 165, 167, 169. The low feed line 183 isconnected to the low motor 41, the intermediate feed line 18d isconnected t-o the i-ntermediate motor 48 and the high clutch line 186 isconnected to the high clutch motor 53 and each is respectively connectedto the .double width feed ports 172, 173 and 174. Reverse line 187connected to reverse motor 62 is similarly connected to feed port 175.The stationary feed ports are all in the bore and the supply and exhaustports are all in the valve element.

With the valve in the reverse low position RL shown, the uid is suppliedfrom ratio supply line 133 via feed port 161 and supply port a to supplypassage 156, through all supply ports b through f and feed ports 162,164, 166 'and 168 and 171 respectively to splitter `low line 181 andthrough supply port g and feed port 175 t-o reverse line 187. Splitterhigh line 182, low line 183, intermediate line 184 and high clutch line186 are connected respectively via exhaust ports h through k to exlhaustpassage 157. On movement of the valve element to the reverse highposition RH, supply port a will move to the upper end of feed port 161and thus ratio supply 'line 133 remains connected to the supply passage156. rl`he supply ports c, d, e and f are connected respectively to feedports 163, 165, 167 and 169 to supply main line pressure to the splitterhigh `line 182. The splitter low line 181 is connected at feed ports 16Sand 171 to exhaust parts lz and ifor exhaust via passage 157. Supplyport g of the supply passage remains connected to reverse feed port 175to supply reverse m-otor 62.

in neutral position, ratio supply line 133 is connected via supply portb to passage 156 and via supply ports c through f to splitter low line151. Splitter high line 182 is connected via exhaust ports h and toexhaust 157. Low port 172, intermediate port 173 and high port 174 areconnected respectively by exhaust lports j, k and l to exhaust 157.Reverse port 175 is connected to the exhaust 18S at the lower end of thevalve bore.

in sixth ratio position 6th supply line 133 is connected through supplyport b to supply passage 156 which supplies through supply ports d, eand f the feed ports 163, 165 and 167 for the splitter high line 182.Supply passage 156 is also connected via supply port g, feed port 174and high clutch line 156 to the high motor 53. Splitter low line 181 isconnected by feed ports 166, 168 `and 171 respectively to exhaust portslz, z' and jto exhaust 157. Low feed port 172 and intermediate feed port173 are connected via exhaust ports k `and l to exhaust 157. Reversefeed port 175 to `connected to exhaust at 188.

In the fth ratio position, ratio supply line 133 is connected via supplyport c to the passage 156 and via supply ports d, e and f to splitterlow `line 181 and via sup-ply port g to the high ratio feed por-t 174iland `line 186. Splitter high line 132 is connected via exhaust ports h,z' and j to exhaust 157 and low Iand intermediate are connected viaexhaust ports k and l to the same exhaust. Reverse remains connected toexhaust 188.

In fourth ratio, ratio supply line 133 is connected via supply port c tosupply Ipassage 156 `and via supply ports e and f to splitter thigh line182. The supply port g is connected to the feed port 173 andintermediate line 184. Now both `the high port 174 and reverse port 175are connected to exhaust 188. The splitter low line 181 is con- 5 nectedby exhaust ports h through k to exhaust 157 and low is connected byexhaust port l to this exhaust.

From the above it is believed clear that in third ratio position 3rd,the ratio supply line is connected via passage 156 to splitter low line181 and intermediate line 184. In second position .'Znd, the supply isconnected to the 10W ratio line 183 and the splitter high line 182. Inrst position 1st, low remains connected and splitter low line 181 isconnected. In ea-ch of these positions all the other lines are connectedto exhaust. The spring deten-t 191 cooperating with a plurality ofgrooves 192 holds the valve element 152 in each of the ratio positions.

The trimmer valve 291 has a valve element 202 and a valve plug 203located in a bore 204 having a reduced diameter portion 205 extending toexhaust 214. A dual spring 266 consists of a first spring 207 land asecond spring 2d@ interconnected by a cup-shaped element 209 providingan internal abutment at the base and an external abutment |at the lipwhich permits the springs to overlap to provide greater yspr-ing lengthin the limited valve bore to reduce the spring rate. The kplug 210 inthe base of the cup 2119 makes it possible to use `a longer cup withsprings of this length to stop movement of plug 203 to -limit thegradual pressure rise to a predetermined value. When the lookup shiftvalve 231 and the lockup cutoff valve 132 are both in lockup positionfor engaging the lockup clutch iine 221 -is supplied with fluid iat mainline pressure to bore 204 to assist spring 206 to bias tihe plug 253 andthe valve 252 to lthe closed position closing the exhaust 214. Underthese conditions, Whenever pressure is Alockup clutch line 111 is ventedto exhaust 144 by operation of the lockup cutoff valve 132, due to theinitiation of filling of a ratio motor, valve 223 regulates to pressurein line 221 connected to hore 2124 at la low value. Then since valve 201is in the position shown, the low pressure in line 133 will move thevalve 262 and plug 2553 down against spring 266 and' the lower pressurein bore 204 to permit exhaust at 214 to regulate the pressure in lline133 at a low value. Simultaneously there will be a slow flow of fluidfrom line 133 through orifice 216 to cavity 217 within the valveelements 262 to gradually separate the valve element 202 and the plug2113 to increase the biasing force provided by spring 256 to graduallyincrease the main line pressure to the main line regulated pressure toprovider soft natio engagement during the gradual pressure rise at lowpressure values. When the main line pressure from line 133 flows intosmall bore 2125 it acts on the free end of valve 2112 and also flowsthrough orifice 216 to fill chamber 217 and act on the other end ofvalve 2112 which is in bore 294 and has a larger area than tlhe freeend. Thus the fluid causes the valve 202 to gradually move away fromplug 203.

The trimmer valve 2111 does not function during converter operation.Valve 223 4maintains sa low pressure in line 221 during conventeroperation since lookup c'lxutch line 111 and its branch 229 areconnected by lockup' cutoff valve 132 to lockup shift line 166 which isconnected by the lookup shift valve ..31 in the downshift or converteroperation position to exhaust 246. This `low pressure in line 221 isinsucient to enable spring 206 to move the plug 263 to the upperlposition shown in contact with valve element 202 to initiate aregulation cycle.

A low signal pressure is supplied by line 221 to the spring chamberportion of bore 204 to assist the spring 266 to provide an additionalbiasing force acting on the plug 203 proportional to throttle pressureduring a ratio change made while the transmission operating W-ith thelockup shift valve upshifted for -lockup clutch engagement pressure andthe same gradual increase of pressure from to provide an initial lowpressure proportional to throttle eao'h initial pressure. Line 221 issup-plied from the ratio supply line 133 by a restricted branch line 222providing a restricted supply to fluid to line 221. The pressure in line221 is Iregulated by a ball regulator valve 223 having a -ball 224biased by a spring 225, Whose biasing force is adjusted by a piston 227whose position is controlled by throttle pressure from lline 96. Abranch 229 of lookup clutch line 11 supplies lookup clutch fiuid to thespring chamber of valve 223 to hold the ball 224 on its seat permittingpressure supplied via line 222 to line 221 to supply line pressure tat arestricted rate of increase to the spring chamber of trimmer valve 201to reset the trimmer valve quickly, but not so fast as to cause shock,to the position Ishown so that it is ready for the next regulatingcycle. When the lookup shift v-alve 231 is down in converter operationposition lookup shift line 166 is exhausted, so lookup clutch line 111is exhausted regardless ofthe position of lookup cutoff valve 132 sovalve 223 supplies low pressure to line 221 which is insufiicient to settrimmer valve 201 for operation. When the lookup shift valve upshifts,main pressure is supplied by line 106, lookup cutoff valve 132 in thenormal position show-n and line 111 to engage the lookup clutch and actvia branch 229 to hold valve 223 to supply main pressure to line 221 toset trim-mer valve 201. On a ratio shift during lookup operation thelookup cutoff valve 132 downshifts to exhaust line 111 to disengage thelookup clutch and exhausts branch 229 so valve 223 supp-lies lowpressure by line 221 to the trimmer valve 201 to, in conjunction withthe drop in main pressure in line 133, start a trimmer valve regulationcycle. On engagement of the ratio the lockutp shift valve upshifts tosupply line 111 to engage the lookup clutch and supply branch 229 sovalve 223 sends main pressure by line 221 to reset the trimmer valve.

The lookup shift valve 231 has a valve element 232 having lands a, b andc of consecutively reduced diameters located in a stepped bore 233. Thespring 236 and throttle pressure connected via line 96 to the springchamber portion of bore 233 biases the valve element 232 to thedownshift position shown with a low biasing force permitting an upshiftdue to governor pressure supplied by governor pressure line 237 actingon governor plug 238 in chamber 239 to act on the valve element toupshift it at a low speed of intermediate shaft 24. When the splitterhigh ratio is engaged, the pressure in line 182 enters bore 241 and actson abutment piston 242 to move the abutment piston against the stopshoulder 243 to increase the biasing force of spring 236 requiring ahigher intermediate shaft speed and governor pressure acting on plug 238to upshiftthe valve element 232. Thus the lookup clutch is engaged atthe same converter output speed in both splitter low and high drives ateach throttle pedal position.

In the downshift position shown, the main line 81 is blocked by the landb and the lookup shift line 106 is connected to exhaust 246 fordisengagement of the lockup clutch. The chamber between the valveelement 232 and governor plug 238 is vented by exhaust 247. Theconverter and brake feed line 91 is connected freely bypassing orifice248 between the lands a and b to the brake feed line 251 and theconverter feed line 252. On an upshift the land b blocksintercommunioation between the brake feed line 251 and the converterfeed line 252 and thus provides full feed to the brake feed line andrestricted feed through orifice 248 to the converter feed line 252. Atthe same time, the main line 81 is connected between the lands b and cto the lookup shift line 106 to engage the lookup clutch if the lookupclutch cutoff valve 132 is in normal position shown. The relief valve253 limits pressure in the converter feed line 252.

The brake valve 261 has a valve element 262 having equal diameter landsa, b and c located in a bore 263 and biased to a brake off position bythe spring 264. The spring chamber is vented by exhaust 266. In thebrake off position shown, the brake feed line 251 is blocked by land a.The brake inlet line 100 and the brake outlet line 101 are connectedrespectively to exhausts 267 and 268. The converter outlet line 250,having nonreturn check valve 285 connects to line 281, and cooler 282.When the brake valve element 262 is moved against spring 264 to thebrake on position, the brake supply line 251 is supplied gradually onflow valve movement due to the tapered land a to the brake inlet line100, and the brake outlet line 101, while remaining connected to thecontinuation thereof to the main line regulator valve, is disconnectedfrom exhaust 268 and connected to the cooler inlet line 281. The coolerinlet line 281 is connected through a cooler 282 and cooler outlet line283 has a lubrication feed branch and a regulator valve 284 limiting thepressure to a low value and connecting the excess liuid to exhaust 286.

Operation With the manual selector valve 152 in neutral, and the engineoperating, the front pump driven by the engine preferably from theconverter pump housing 4 in a conventional manner will supply liuid tothe main line 81 which will be regulated by the regulator 82 asexplained above. The manual selector valve 151 will supply main linepressure from the ratio supply line 133 to the splitter low line 181 toactuate the splitter low motor 28 to engage the splitter low brake 27 toprovide low ratio in the splitter gear unit. All the ratio motors in therear unit are disengaged since their supply lines are connected toexhaust by the manual selector valve 151. This provides a positiveneutral. The lookup clutch shift valve 231 will be in the downshiftposition shown providing full brake and converter supply via lines 251and 252 and blocking the supply to the lookup shift line 106.

On a shift to first ratio the manual selector valve maintains theconnection from the ratio supply line to the splitter low line 181 andprovides a connection to the low line 183 to aotuate the low motor 41 toengage the low brake 39 to provide low ratio in the transmission. Thefiow of fluid to engage low ratio passing through orifice 131 shiftslookup cutoff valve 132 to cut off the connection between the lookupshift line 106 and the lockup clutch line 111 and to connect lookupclutch line 111 to exhaust 114 to insure disengagement of the lookupclutch and to exhaust the pressure from the spring chamber of valve 223via exhaust 144 to condition the signal pressure regulator valve 223 toregulate the pressure in line 221 at a low pressure proportionate tothrottle pedal position and thus condition the trimmer valve 201 foroperation. When the transmission is in lookup drive, during each ratioengagement the trimmer valve controls the pressure in line 133 toprovide an initial low pressure proportional to torque demand and thongradually increases the pressure until the drive is engaged and slipstops and then more quickly raises the pressure to main line pressurefor engaging the ratio motor with a soft initial engagement and anonslip final engagement. On shifts made while the converter isoperating, since the lookup shift valve 231 has not upshifted, thetrimmer valve is not set and does not function to reduce main pressureand shifting.

The manual selector valve may be moved to each of the six forward andtwo reverse positions as explained' above to provide these ratios. Oneach shift the lookup clutch cutoff valve acts on the above initialshift to first ratio to condition the trimmer valve 201 to control thepressure for gradual engagement of the ratio.

When the transmission is in first, third, fifth and reverse low ratiossplitter low is engaged and splitter high line 182 is exhausted at themanual valve 151, so the abutment plug 242 of lookup shift valve 231 isin the upper position shown providing a lookup shift at a lowintermediate shaft speed varying with throttle pressure supplied by line96. When the transmission is in second, fourth, sixth and reverse highmain line pressure is supplied to line 182 to engage the splitter highratio and this pressure acts on the abutment plug 242 to move it to thestop shoulder 243 to increase the biasing force of spring 236 to providea lookup shift at a higher speed, having the same proportion the lowerspeed shift point 9 as the proportion of the change in intermediateshift speed provided by the splitter low to splitter high shift. Thethrottle pressure in line 96 is always less than main line pressure sothat it does not prevent operation of abutment plug 242 by main linepressure.

The above described preferred embodiment is illustrative of theinvention defined in the appended claims.

We claim:

l. In a transmission, a multiratio gear unit having a plurality of fluidactuated ratio establishing devices engaged in a plurality of pairs toprovide a plurality of ratios, a source of -lluid under pressure, ashift valve means operably connecting said source to each of saidplurality of iluid actuated ratio establishing devices having a valveelement reciprocably mounted in a bore, said valve element including alongitudinal blind passage having a plurality of supply ports, andlongitudinal exhaust passage means having a plurality of exhaust ports,said bore having a plurality of feed ports, said supply and exhaust andfeed ports being arranged to selectively connect said source to pairs ofsaid fluid actuated ratio establishing devices and to connect the otherratio establishing devices to said exhaust passage means.

2. In a control for supplying a plurality of lluid actuated devicesactuated in a plurality of pairs, a source of fluid under pressure,valve means operably connecting said source to each of said plurality ofiluid actuated devices having a valve element reciprocably mounted in abore, said valve element including a longitudinal blind passage closedat both ends and having a plurality of supply ports, and longitudinalexhaust passage means having a plurality of exhaust ports, said borehaving a plurality of feed ports with one connected to said source andthe others connected to said fluid actuated devices, said supply andexhaust and feed ports being arranged to selectively connect said sourceto pairs of said iluid actuated devices and to connect the other fluidactuated devices to said exhaust passage means.

3. In a valve for connecting a source to eac-h of said plurality offluid actuated devices, a valve body having a bore, a valve elementreciprocally mounted in said bore, said valve element including alongitudinal blind passage closed at both ends and having a plurality ofsupply ports, and exhaust means including a longitudinal exhaust passagehaving a plurality of exhaust ports, said bore having a source port forconnection to a source and a plurality of feed ports for connection to aplurality of fluid actuated devices, said supply, exhaust, source and`feed ports being arranged to connect said source port to said blindpassage to selectively connect said source port through said blindpassage to selected pairs of said feed ports and to connect the otherfeed port to said exhaust means.

4. In a control, a plurality of fluid actuated devices actuated in aplurality of pairs, a source of fluid under pressure, valve meansoperably connecting said source to each of said plurality of fluidactuated devices having a valve element reciprocally mounted in a bore,said valve element including a longitudinal blind passage closed at bothends and having a plurality of supply ports, and a longitudinal exhaustpassage means having a plurality of exhaust ports exhausting at bothends of said valve element, said bore having a plurality of feed portswith one connected to said source and the others connected respectivelyto said lluid actuated devices, said supply and exhaust and feed portsbeing arranged to connect said one feed port to said blind passage inall valve positions and to selectively connect said source via pairs ofsupply ports and feed ports to pairs of said fluid actuated devices andto connect the `other fluid actuated devices via their feed ports tosaid exhaust passa-ge means.

5. `In a valve, a valve body having a bore and a source port and aplurality of feed ports, a valve element reciprocally mounted in saidbore, said valve element including a longitudinal blind passage closedat both ends and having a plurality of supply ports, and longitudinalexhaust passage means having a plurality lof exhaust ports, said supply,exhaust source, and feed ports being arranged with one supply portconnected to said source port in all valve positions and the othersupply ports connected to supply said feed ports in selected pairs ineach position of the valve element and the other feed ports beingconnected by said exhaust ports to exhaust to selectively connect saidsource to pairs of said feed ports and to connect the other feed portsto said exhaust passage means.

6. In a transmission; an input shaft; a converter shaft; an intermediateshaft; an output shaft; a torque converter and a fluid operated lookupclutch connecting said input shaft to said converter shaft; a -rst gearunit connecting said converter shaft to said intermediate shaft having alow ratio and a high ratio fluid operated drive establishing meansselectively operable to provide low and high drive ratios; a secondmultiratio gear unit connecting said intermediate shaft to said outputshaft having a plurality of fluid operated drive establishing meansselectively operable to provide a plurality of ratios; a source of fluidunder pressure; governor means providing a governor pressureproportional to intermediate shaft speed; torque demand means providinga torque demand pressure proportional to torque demand; a lookup shiftval-ve having a valve element Igovernor pressure responsive meansoperatively connected to said governor means to receive Igovernorpressure to move said valve for upshift, a shift pressure controlledspring abut-ment, a biasing spring between said valve element and saidspring abutment urging said valve element to downshift and a lclosedchamber between said valve element and spring abutment connected to saidtorque demand means to receive said torque demand pressure for acting onsaid valve element operative in response to governor pressure overcomingsaid biasing pressure and torque demand pressure at a predeterminedspeed to connect said source to said lockup clutch to engage said lookupclutch; selector valve means operably connected to said source and tosaid fluid operated drive establishing means of said rst and second gearunits to selectively connect said source to pairs of said driveestablishing means to provide a plurality of drive ratios and includingmeans operative when fluid is connected to said high ratio fluidoperated drive establishing means operative to supply pressure to saidshift pressure controlled abutment to move said abutment a controlleddistance to increase the biasing force o-f said biasing spring tocontrol said locku-p shift valve to provide an upshift to engage thelookup clutch at a predetermined higher governor speed and pressure.

7. In a transmission; multiratio drive means including a plurality offluid operated ratio establishing devices; a source of fluid underpressure; selector valve means connecting said source to said iluidoperated ratio establishing devices selectively operable to selectivelyconnect said source to said fluid operated ratio establishing devices; aregulator valve having, a bore, a valve element and a valve plug locatedin the bore, means between said valve element and valve 1plug providinga chamber, and biasing means engaging said valve plug to move said valveplug and valve element in a valve closing direction; said valve elementcontrolling the exhaust of fluid from said source to regulate thepressure of said source; said source being connected by a rstrestriction to said expanding chamber; Illuid operated means operativeon receiving iluid to provide an additional biasing force on said valveplug and valve element in the same direction as said biasing means; apassage, a second restriction connecting said source to said passageoperative to supply a restricted llow of fluid to said fluid operatedmeans; a second regulator valve operative to control the pressure of thefluid in said supply passage at a pressure proportional to torquedemand.

8. In a transmission; drive means for establishing a drive; a controlsystem including fluid actuator means connected to said drive means forestablishing said drive means in response to the supply of fluid to saidfiuid actuator means; fluid supply means connected to said fluidactuator means to supply fiuid to said fluid actuator means to establishsaid drive means; and a regulator valve including a valve body having abore with a closed end, a first valve element having one face facing theclosed end of said bore providing an area on which fluid acts and anopposite face providing a larger area on which fluid acts; a secondvalve element having a iface adjacent said first valve element, biasingmeans biasing said second valve element into engagement with said firstvalve element and both valve elements toward said closed end of saidbore, an exhaust port in said bore, said bore having inlet port meansconnecting said source to said bore to act on said one face to move saidvalve element against said biasing means to open said exhaust toregulate the pressure of said source, means connecting said source tosaid bore between aid first and second valve elements to slowly supplyfluid between said valve elements to slowly increase the regulatedpressure.

9. In a transmission; drive means for establishing a drive; a controlsystem including fiuid actuator means connected to said drive means forestablishing said drive means in response to the supply of fluid to saidfiuid actuator means; liuid supply means to supply fiuid under pressureto said fiuid actuator means; and a regulator valve including a valvebody having a bore with a closed end, a first valve element having oneface facing the closed end of said bore providing an area on which fluidacts and an opposite face providing a large area on which fluid acts, anorifice extending through said first valve element from said one face tosaid opposite face, a second valve element reciprocally mounted in saidbore for engagement with said first valve element and having an adjacentface facing said first valve element, an inlet port connected to saidliuid supply means located at the closed end of said bore to act on saidone end face and pass through said orifice to act on said opposite endface and the adjacent vface of said second valve element, an exhaustport spaced from said inlet port, variable biasing means engaging saidsecond valve element with a high force to urge said first and secondvalve element toward the closed end of said bore against fiuid underpressure acting on said adjacent face of said second valve element andcontrollable to reduce the biasing force to provide regulation at aninitial low pressure and a gradually increasing pressure and then toincrease the biasing force to said high force.

10. In a transmission; drive means for establishing a drive; a controlsystem including fluid actuator means connected to said drive means forestablishing said drive means in response to the supply of fiuid to saidfiuid actuator means; fiuid supply means to supply fiuid under pressureto said fiuid actuator means; and a regulator valve including a valvebody having a bore with a closed end and a reduced diameter portionadjacent said closed end, a first valve element having a small diameterportion fitting said small diameter bore portion and a larger diameterportion fitting said bore, an orifice extending through said first valveelement, a second valve element reciprocally mounted in said bore forengagement with said first valve element, biasing means engaging saidsecond valve element to urge said first and second valve element towardthe closed end of said bore, an inlet port connected to said fluidsupply means located at the closed end of said bore, and an exhaust portspaced from said inlet port.

11. The invention defined in claim 10 and said biasing means includingmeans operative in one control condition to bias both valve elements tothe closed end of said bore to block said exhaust port and operative ina second control condition to reduce the force of said biasing means toinitially provide a low pressure and operative in a third controlcondition to provide insufiicient biasing force to move both said valveelements to said closed end of said bore to render said regulating valveinoperative.

12. The invention defined in claim 10 and said biasing means includingmeans operative in one control condition to bias said second valveelement into operative engagement with said first valve element and saidfirst valve element toward the closed end of said bore to close saidexhaust port to render said regulator valve operative to regulate, andoperative in a second control condition to provide insufficient biasingforce to bias said second valve element into operative engagement withsaid first valve element to render said regulator valve inoperative toregulate and operative in a third control condition only following saidfirst condition to cause said regulator valve to initiate regulation ata low pressure and to gradually increase the pressure.

References Cited by the Examiner UNITED STATES PATENTS 1,765,090 6/1930Morin 251-76 2,244,213 6/1941 Patton 277-57 2,869,400 1/1959 Langdon74-765 DAVID I. WILLIAMOWSKY, Primary Examiner.

DON A. WAITE, Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No 3 ,293,934 December 27 1966 Robert H. Schaefer et al.

It is hereby certified that error appears in the above numbered patentrequiring correction and that the said Letters Patent should read ascorrected below.

Column 5, line 38 for "parts" read ports line 60, for "to", firstoccurrence, read is column 6, line 30 for "is" read inv line 33, for"to" read the line 69, beginning with "pressure" strike out all to andincluding "throttle" in line '70, same column 6, and insert instead toprovide an initial low pressure proportional to throttle pressure andthe same gradual increase of pressure from line 73, for "to" read ofcolumn 7 line 3 for "ll" read lll column 9,

line l for "shift" read shaft Signed and sealed this 26th day ofSeptember 1967 (SEAL) Attest:

ERNEST W. SWIDER EDWARD J BRENNER Attesting Officer Commissioner ofPatents

6. IN A TRANSMISSION; AN INPUT SHAFT; A CONVETER SHAFT; AN INTERMEDIATESHAFT; AN OUTPUT SHAFT; A TORQUE CONVERTER AND A FLUID OPERATED LOCKUPCLUTCH CONNECTING SAID INPUT SHAFT TO SAID CONVERTER SHAFT; A FIRST GEARUNIT CONNECTING SAID CONVERTER SHAFT TO SAID INTERMEDIATE SHAFT HAVING ALOW RATIO AND A HIGH RATIO FLUID OPERATED DRIVE ESTABLISHING MEANSSELECTIVELY OPERABLE TO PROVIDE LOW AND HIGH DRIVE RATIOS; A SECONDMULTIRATIO GEAR UNIT CONNECTING SAID INTERMEDIATE SHAFT TO SAID OUTPUTSHAFT HAVING A PLURALITY OF FLUID OPERATED DRIVE ESTABLISHING MEANSSELECTIVELY OPERABLE TO PROVIDE A PLURALITY OF RATIOS; A SOURCE OF FLUIDUNDER PRESSURE; GOVERNOR MEANS PROVIDING A GOVERNOR PRESSUREPROPORTIONAL TO INTERMEDIATE SHAFT SPEED; TORQUE DEMAND MEANS PROVIDINGA TORQUE DEMAND PRESSURE PROPORTIONAL TO TORQUE DEMAND; A LOCKUP SHIFTVALVE HAVING A VALVE ELEMENT GOVERNOR PRESSURE RESPONSIVE MEANSOPERATIVELY CONNECTED TO SAID GOVERNOR MEANS TO RECEIVE GOVERNORPRESSURE TO MOVE SAID VALVE FOR UPSHIFT, A SHIFT PRESSURE CONTROLLEDSPRING ABUTMENT, A BIASING SPRING BETWEEN SAID VALVE ELEMENT AND SAIDSPRING ABUTMENT URGING SAID VALVE ELEMENT TO DOWNSHIFT AND A CLOSEDCHAMBER BETWEEN SAID VALVE ELEMENT AND SPRING ABUTMENT CONNECTED TO SAIDTORQUE DEMAND MEANS TO RECEIVE SAID TORQUE DE-